Planetary gear assembly for drum washing machine and drum washing machine

ABSTRACT

A planetary gear assembly for a drum washing machine and a washing machine are provided. The planetary gear assembly includes a planetary gear component. The planetary gear component includes a planet carrier, a plurality of planetary gears rotatably mounted to the planet carrier separately and configured to be meshed with a main shaft separately, the main shaft being configured to drive a drum to rotate in a drum washing machine; and a planetary gear outer teeth casing fitted over an outer side of the plurality of planetary gears, meshed with the plurality of planetary gears separately, and configured to be in transmission connection with an agitator in the drum.

CROSS-REFERENCES TO RELATED APPLICATIONS

The present disclosure is a national phase application of InternationalApplication No. PCT/CN2018/089334, filed on May 31, 2018, which claimsthe priority of Chinese Application No. 201820221165.5 and201810122495.3, filed in the Chinese Patent Office on Feb. 7, 2018, theentireties of which are herein incorporated by reference.

FIELD

The present disclosure relates to the field of laundry treatmentdevices, and more particularly to a planetary gear assembly for a drumwashing machine and a drum washing machine.

BACKGROUND

When laundry is washed in a drum washing machine, a drum is rotated todrive the laundry and water in the drum to rotate and wash the laundry,and the laundry is lifted up and down by a baffle in the drum and isdropped by an inner circumferential surface of the drum. However, due toa single washing mode, the washing effect is affected. Therefore, thereis a need for improvement.

To this end, a drum washing machine provided with an impeller in a drumis proposed in a related art. For example, PCT/CN2016/11037 discloses adrum-type washing machine, in which the impeller is directly driven torotate by an electric motor while the electric motor drives the drum torotate by means of transmission of a planetary gear mechanism, and arotational speed of the drum is less than a rotational speed of theimpeller. However, since the drum itself has a larger volume than theimpeller does, and the drum is required to carry the laundry and thewater during washing, the planetary gear mechanism has a relativelylarge load, to affect the effect of transmission of power by theplanetary gear mechanism and the service life thereof.

SUMMARY

The present disclosure seeks to solve at least one of the problemsexisting in the related art to at least some extent. To this end, thepresent disclosure proposes a planetary gear assembly for a drum washingmachine, the planetary gear assembly can transmit a torque of a mainshaft to an agitator, to dually drive a drum and the agitator, and the aplanetary gear assembly can transmit power stably and has a long servicelife, or the like.

The present disclosure further proposes a drum washing machine havingthe planetary gear assembly.

The planetary gear assembly for a drum washing machine according toembodiments of a first aspect of the present disclosure includes aplanetary gear component. The planetary gear component includes: aplanet carrier; a plurality of planetary gears rotatably mounted to theplanet carrier separately and configured to be meshed with a main shaftseparately, the main shaft being configured to drive a drum to rotate ina drum washing machine; and a planetary gear outer teeth casing fittedover an outer side of the plurality of planetary gears, meshed with theplurality of planetary gears separately, and configured to be intransmission connection with an agitator in the drum.

In the planetary gear assembly for a drum washing machine according toembodiments of the present disclosure, by providing the planetary gearassembly between the main shaft and the agitator, the torque of the mainshaft can be transmitted to the agitator to drive the agitator torotate, the rotation of the agitator may be combined with the rotationof the drum into various washing modes, for example, only one of theagitator and the drum is rotated or the agitator and the drum arerotated at the same time, or in the same direction, or in oppositedirections, to diversify the washing mode of the drum washing machine.

Moreover, the torque of the main shaft is transmitted to the agitator bythe planetary gear assembly, the agitator can be indirectly driven usingthe driver. Since the load at the agitator is much less than the load atthe drum, compared with a drum washing machine with an impeller(agitator) in the related art, the load acting on the planetary gearassembly is greatly reduced, which not only facilitates stable powertransmission to improve the performance stability of the drum washingmachine, but also greatly reduces the risk of damage to the planetarygear assembly, to prolong the service life of the drum washing machine.

According to an embodiment of the present disclosure, when the planetcarrier is allowed to rotate freely, the plurality of planetary gearstransmit a torque of the main shaft to the planetary gear outer teethcasing in a same direction, and when the planet carrier is braked, theplurality of planetary gears transmit the torque of the main shaft tothe planetary gear outer teeth casing in an opposite direction.

In one embodiment, when the planet carrier is braked, a rotational speedof the planetary gear outer teeth casing is less than a rotational speedof the main shaft.

In one embodiment, when the planet carrier is allowed to rotate freely,a rotational speed of the planetary gear outer teeth casing is equal toa rotational speed of the main shaft.

According to an embodiment of the present disclosure, the planet carrierincludes a planetary gear support, the plurality of planetary gears arerotatably mounted on a side face of the planetary gear support, and theside face of the planetary gear support is provided with a plurality ofmounting bosses; and a planetary gear fixing disk mounted on theplurality of mounting bosses.

In one embodiment, the planetary gear support and the planetary gearfixing disk are both located in the planetary gear outer teeth casing,and the planetary gear support and the planetary gear fixing disk arestopped at two sides of internal teeth of the planetary gear outer teethcasing respectively to be positioned in an axial direction of theplanetary gear outer teeth casing.

In one embodiment, the side face of the planetary gear support isprovided with a plurality of planetary gear mounting seats, each of theplanetary gear seats is provided with a planetary gear fixing shaft, andthe plurality of planetary gears are rotatably mounted to the pluralityof planetary gear fixing shafts in one-to-one correspondencerespectively.

In one embodiment, the plurality of mounting bosses and the plurality ofplanetary gears are arranged alternately in a circumferential directionof the planetary gear support, each of the mounting bosses is providedwith a positioning column, the planetary gear fixing disk is providedwith a plurality of positioning holes, and positioning columns on theplurality of mounting bosses are fitted in the plurality of positioningholes in one-to-one correspondence.

According to an embodiment of the present disclosure, the planetary gearassembly further includes a planetary gear casing, the planetary gearcomponent is provided in the planetary gear casing, and the planetarygear outer teeth casing is in transmission connection with the agitatorvia the planetary gear casing.

In one embodiment, one of an inner peripheral wall of the planetary gearcasing and an outer peripheral wall of the planetary gear outer teethcasing is provided with a flange, the other one of the inner peripheralwall of the planetary gear casing and the outer peripheral wall of theplanetary gear outer teeth casing is provided with a latching slot, andthe flange is fitted in the latching slot.

In one embodiment, the outer peripheral wall of the planetary gear outerteeth casing is provided with a plurality of flanges, each of theflanges extends in an axial direction of the planetary gear outer teethcasing, the plurality of flanges are spaced apart from each other in acircumferential direction of the planetary gear outer teeth casing, theinner peripheral wall of the planetary gear casing is provided with aplurality of latching slots, each of the latching slots extends in anaxial direction of the planetary gear casing, the plurality of latchingslots are spaced apart from each other in a circumferential direction ofthe planetary gear casing, and the plurality of flanges are fitted inthe plurality of latching slots in one-to-one correspondence.

According to a further embodiment of the present disclosure, theplanetary gear assembly further includes: a planetary gear bearingprovided in the planetary gear casing and located on an outer side ofthe planetary gear component, an inner ring of the planetary gearbearing is fitted over the main shaft and rotates with the main shaft,an outer ring of the planetary gear bearing is connected to theplanetary gear casing and rotates with the planetary gear casing.

In one embodiment, an inner peripheral surface of the planet carrier isprovided with meshing teeth meshing with a second shaft in the mainshaft.

Furthermore, the planetary gear assembly further includes a second shaftend bearing, the planetary gear casing is provided with a through hole,the second shaft passes through the through hole, and the second shaftend bearing is provided in the through hole and configured to supportthe second shaft.

In some examples, the planetary gear assembly further includes a shaftsealing member located in the through hole and at an outer side of thesecond shaft end bearing, and configured to seal a gap between thesecond shaft and the planetary gear casing.

The drum washing machine according to embodiments of a second aspect ofthe present disclosure includes the planetary gear assembly for a drumwashing machine according to the above embodiments.

BRIEF DESCRIPTION OF THE DRAWINGS

Embodiments of the present disclosure will become apparent and readilyappreciated from the following descriptions made with reference to thedrawings.

FIG. 1 is a schematic view of a drum washing machine according to anembodiment of the present disclosure;

FIG. 2 is a schematic view of a drum of a drum washing machine mountedon a drum support;

FIG. 3 is an exploded view before the drum support is assembled with amain shaft, a second shaft, a planetary gear assembly of the drumwashing machine, or the like;

FIG. 4 is an assembly view of a main shaft, a main shaft sleeve and amain shaft flange of the drum washing machine;

FIG. 5 is an exploded view of the structure shown in FIG. 4 ;

FIG. 6 is a schematic view of a planetary gear assembly and a wearsleeve of the drum washing machine;

FIG. 7 is an exploded view of the planetary gear assembly of the drumwashing machine;

FIG. 8 is an exploded view of a planetary gear component of the drumwashing machine;

FIG. 9 is an exploded view before a planet carrier and a planetary gearshown in FIG. 8 are assembled;

FIG. 10 is a schematic assembly view of the planet carrier and theplanetary gear shown in FIG. 8 ;

FIG. 11 is a schematic view of a planetary gear casing shown in FIG. 7 ;

FIG. 12 is a rear view of a local structure of a drum washing machineaccording to an embodiment of the present disclosure;

FIG. 13 is a schematic view of a brake shown in FIG. 12 ;

FIG. 14 is an exploded view of a brake shown in FIG. 12 ;

FIG. 15 is a schematic view of a brake lever shown in FIG. 12 ;

FIG. 16 is a sectional view taken along line A-A in FIG. 15 ;

FIG. 17 is a schematic view of a drum washing machine viewed from thefront to the rear, with a cabinet, drum and agitator removed;

FIG. 18 is an enlarged view of portion I shown in FIG. 17 ;

FIG. 19 is a schematic view of a drum washing machine viewed from therear to the front, with a cabinet, drum and agitator removed;

FIG. 20 is an enlarged view of portion II shown in FIG. 19 ;

FIG. 21 is a sectional view taken along line B-B in FIG. 19 ;

FIG. 22 is a schematic view of a drum washing machine viewed from thefront to the rear, with a cabinet, drum and agitator removed;

FIG. 23 is a sectional view taken along line C-C in FIG. 22

REFERENCE NUMERALS

drum washing machine 100,

tub 1, mounting hole 11, main shaft bearing seat 12,

drum 2, drum support 201, central shaft portion 2011, support portion2012, drum body 21, rear cover 22 of the drum,

main shaft 31, cavity 311, pulley 312, belt 3121, lock nut 313, mainshaft bearing 314, main shaft flange 315, main shaft sleeve 316,

second shaft 32, water supply passage 320, second shaft bearing 3211,second shaft end bearing 3212, brake disk 322, adapter 323, adapterbearing 3231, adapter sealing member 3232, wear ring 324, shaft sealingmember 325,

agitator 4, water spray hole 41, water collection cavity 42, waterdividing passage 43, rib 44,

electric motor 5, electric motor shaft 51,

planetary gear assembly 6,

planetary gear component 61, planet carrier 611, planetary gear support6111, mounting boss 6112, positioning column 6113, planetary gearmounting seat 6114, planetary gear fixing shaft 6115, planetary gearfixing disk 6116, positioning hole 6117, limiting hole 6118, planetarygear 612, planetary gear outer teeth casing 613, flange 6131,

planetary gear casing 62, latching slot 621, through hole 622,

planetary gear bearing 63, assembly sealing member 641, wear sleeve 642,

brake 7,

sliding groove seat 71, slideway 711, limiting boss 712,circumferentially positioned sliding groove 713, support sliding groove714, via hole 715,

brake lever 72, limiting block 720, slideway fitting portion 721, axialreinforcing rib 7211, transmission portion 722, bridge portion 723,transverse reinforcing rib 7231, longitudinal reinforcing rib 7232,brake portion 724, straight sliding groove 725,

brake driver 73, brake cam 74, eccentric column 741, brake support 75,limiting sliding groove 751.

DETAILED DESCRIPTION OF THE DISCLOSURE

Reference will be made in detail to embodiments of the presentdisclosure, and the examples of the embodiments are illustrated in thedrawings, and the same or similar elements and the elements having sameor similar functions are denoted by like reference numerals throughoutthe descriptions. The embodiments described herein with reference todrawings are illustrative, and merely used to explain the presentdisclosure. The embodiments shall not be construed to limit the presentdisclosure.

In the description of the present disclosure, it is to be understoodthat terms such as “center”, “longitudinal,” “transversal,” “length”,“width”, “thickness”, “upper”, “lower”, “front”, “rear”, “left”,“right”, “vertical”, “horizontal”, “top”, “bottom”, “inner”, “outer”,“clockwise”, “anticlockwise”, “axial”, “radial”, and “circumferential”should be construed to refer to the orientation as then described or asshown in the drawings under discussion. These relative terms are forconvenience of description and do not require that the presentdisclosure be constructed or operated in a particular orientation, thuscannot be construed to limit the present disclosure. Furthermore, thefeature defined with “first” and “second” may include one or more ofthis feature explicitly or implicitly. In the description of the presentdisclosure, the term “a plurality of” means two or more unless otherwisestated.

In the description of the present disclosure, it should be noted thatunless specified or limited otherwise, the terms “mounted”, “connected”,and “coupled” and the like are used broadly, and may be, for example,fixed connections, detachable connections, or integral connections; mayalso be mechanical or electrical connections; may also be directconnections or indirect connections via intervening structures; may alsobe inner communications of two elements.

A planetary gear assembly for a drum washing machine according toembodiments of the present disclosure will be described below withreference to FIGS. 1 to 23 .

As shown in FIGS. 1 to 23 , the planetary gear assembly 6 for a drumwashing machine according to embodiments of the present disclosureincludes a planetary gear component 61.

The planetary gear component 61 includes a planet carrier 611, aplurality of planetary gears 612, and a planetary gear outer teethcasing 613. The plurality of planetary gears 612 are rotatably mountedto the planet carrier 611 respectively, and the plurality of planetarygears 612 are configured to be meshed with a main shaft 31 for drivingthe a drum 2 to rotate The planetary gear outer teeth casing 613 isfitted over the plurality of planetary gears 612, and the planetary gearouter teeth casing 613 meshes with the plurality of planetary gears 612respectively, and the planetary gear outer teeth casing 613 isconfigured to be in transmission connection with the agitator 4.

In the planetary gear assembly 6 for a drum washing machine according toembodiments of the present disclosure, by providing the planetary gearassembly 6 between the main shaft 31 and the agitator 4, the torque ofthe main shaft 31 can be transmitted to the agitator 4 to drive theagitator 4 to rotate, the rotation of the agitator 4 may be combinedwith the rotation of the drum 2 into various washing modes, for example,only one of the agitator 4 and the drum 2 is rotated or the agitator 4and the drum 2 are rotated at the same time, or in the same direction orin opposite directions, to diversify the washing mode of the drumwashing machine 100.

Moreover, the torque of the main shaft 31 is transmitted to the agitatorby the planetary gear assembly 6, and the agitator 4 is driven by thedriver indirectly. Since the load of the agitator 4 is much less thanthe load of the drum 2, compared with the drum washing machine with animpeller (agitator) in the related art, the load acting on the planetarygear assembly 6 is greatly reduced, which not only facilitates stablepower transmission to improve the performance stability of the drumwashing machine 100, but also greatly reduces the risk of damage to theplanetary gear assembly 6 to prolong the service life of the drumwashing machine 100.

According to an embodiment of the present disclosure, when the planetcarrier 611 is allowed to rotate freely, the plurality of planetarygears 612 transmit a torque of the main shaft 31 to the planetary gearouter teeth casing 613 in a same direction. When the planet carrier 611is braked, the plurality of planetary gears 612 transmit the torque ofthe main shaft 31 to the planetary gear outer teeth casing 613 inopposite directions.

For example, when the drum washing machine 100 is in a spin mode, theplanet carrier 611 can be switched to be allowed to rotate freely, andthe agitator 4 and the drum 2 are driven to rotate in the same directionby the planetary gear outer teeth casing 613, ensuring that the laundrywill not be entangled or torn when spinning at a high speed.

When the drum washing machine 100 is in a wash mode, the planet carrier611 is braked, and the agitator 4 and the drum 2 are driven to rotate inopposite directions by the planetary gear outer teeth casing 613, toagitate the laundry and water thoroughly to improve the effect ofcleaning the laundry.

In one embodiment, the combination of the state switching of the planetcarrier 611 of the planetary gear assembly 6 and the current mode of thedrum washing machine 100 is not limited to the above-mentionedembodiments, and the free rotation state and the braking state of theplanet carrier 611 may also be combined with any one of the spin andwash modes.

In some examples, when the planet carrier 611 is braked, the rotationalspeed of the planetary gear outer teeth casing 613 is less than therotational speed of the main shaft 31. That is, when the planet carrier611 is braked, the variable-speed transmission of power is implemented.Thus, when the laundry and the water are sufficiently agitated, thelaundry is prevented from being entangled, and the stability and noisereduction of the whole machine are contributed.

In some examples, when the planet carrier 611 is allowed to rotatefreely, the rotational speed of the planetary gear outer teeth casing613 is equal to the rotational speed of the main shaft 31. That is, whenthe planet carrier 611 is allowed to rotate freely, the agitator 4 isrotated in synchronization with the drum 2 (at the same speed and in thesame direction).

Referring to FIGS. 8 to 10 , the planet carrier 611 includes a planetarygear support 6111 and a planetary gear fixing disk 6116. A plurality ofplanetary gears 612 are rotatably mounted on one side face of theplanetary gear support 6111, and one side face of the planetary gearsupport 6111 is provided with a plurality of mounting bosses 6112. Theplanetary gear fixing disk 6116 is mounted on the plurality of mountingbosses 6112, which facilitates the connection of the planetary gearsupport 6111 and the planetary gear fixing disk 6116.

In some examples, the planetary gear support 6111 and the planetary gearfixing disk 6116 are both located in the planetary gear outer teethcasing 613, and the planetary gear support 6111 and the planetary gearfixing disk 6116 are stopped at two sides of internal teeth of theplanetary gear outer teeth casing 613 respectively, to position in anaxial direction of the planetary gear outer teeth casing 613 by means ofthe internal teeth end of the planetary gear outer teeth casing 613. Theplurality of planetary gears 612 may be positioned and mounted by theplanetary gear support 6111. The combined structure of the planetarygear support 6111 and the planetary gear fixing disk 6116 may define theplurality of planetary gears between the planetary gear support 6111 andthe planetary gear fixing disk 6116, realizing modular assembly of thestructure, a more compact structure and convenient assembly.

In some examples, the planetary gear fixing disk 6116 is provided in theplanetary gear outer teeth casing 613 and is secured to the planetarygear support 6111 by a fastener for reliable connection.

In some examples, a side face of the planetary gear support 6111 isprovided with a plurality of planetary gear mounting seats 6114, andeach of the planetary gear seats 6114 is provided with a planetary gearfixing shaft 6115, and the plurality of planetary gears 612 arerotatable respectively and mounted in one-to-one correspondence to theplurality of planetary gear fixing shafts 6115. Here, “one-to-onecorrespondence” may be construed as the equal number of planetary gears612 and planetary gear mounting seats 6114, and each of the planetarygear mounting seats 6114 is provided with one planetary gear 612.

In some examples, the planetary gear mounting seat 6114 is provided witha plughole, one end of the planetary gear fixing shaft 6115 is insertedinto the plughole of the planetary gear mounting seat 6114, and theother end of the planetary gear fixing shaft 6115 is placed in alimiting hole 6118 of the planetary gear fixing disk 6116, to positionand mounting the planetary gear 612.

In some examples, a side face of the planetary gear support 6111 isprovided with a plurality of mounting bosses 6112 and a plurality ofplanetary gear mounting seats 6114, the plurality of mounting bosses6112 and the plurality of planetary gear mounting seats 6114 arearranged alternately in a circumferential direction of the planetarygear support 6111, and the plurality of mounting bosses 6112 and theplurality of planetary gears 612 are arranged alternately in acircumferential direction of the planetary gear support 6111.

Furthermore, each of the mounting bosses 6112 is provided with apositioning column 6113, the planetary gear fixing disk 6116 is providedwith a plurality of positioning holes 6117, the positioning columns 6113on the plurality of mounting bosses 6112 are in a close fit or welded inthe plurality of positioning holes 6117 in one-to-one correspondence,and the planetary gear fixing disk 6116 is supported on the plurality ofmounting bosses 6112, to implement the assembly of the planetary gearfixing disk 6116 and the planetary gear support 6111, with convenientconnection.

As shown in FIGS. 7, 8, and 11 , according to a further embodiment ofthe present disclosure, the planetary gear assembly 6 further includes:a planetary gear casing 62 which is provided therein with the planetarygear component 61 to implement the modular design of the planetary gearassembly 6. The planetary gear outer teeth casing 613 is in transmissionconnection with the agitator 4 via the planetary gear casing 62. Forexample, the planetary gear casing 62 and the agitator 4 may be combinedby screws, and the planetary gear outer teeth casing 613, the planetarygear casing 62 and the agitator 4 are fixedly connected to realizesynchronous operation and facilitate the planetary gear assembly 6 totransmit the torque of the main shaft 31 to the agitator 4.

In some examples, one of an inner peripheral wall of the planetary gearcasing 62 and an outer peripheral wall of the planetary gear outer teethcasing 613 is provided with a flange 6131, the other of the innerperipheral wall of the planetary gear casing 62 and the outer peripheralwall of the planetary gear outer teeth casing 613 is provided with alatching slot 621, and the flange 6131 is fitted in the latching slot621 to ensure a fixed connection between the planetary gear casing 62and the planetary gear outer teeth casing 613.

In some examples, the outer peripheral wall of the planetary gear outerteeth casing 613 is provided with a plurality of flanges 6131, each ofthe flanges 6131 extends in the axial direction of the planetary gearouter teeth casing 613, and the plurality of flanges 6131 are arrangedat intervals in the circumferential direction of the planetary gearouter teeth casing 613.

Correspondingly, the inner peripheral wall of the planetary gear casing62 is provided with a plurality of latching slots 621. Each of thelatching slots 621 extends in the axial direction of the planetary gearcasing 62, and the plurality of latching slots 621 are arranged atintervals in the circumferential direction of the planetary gear casing62. The plurality of flanges 6131 are fitted in the plurality oflatching slots 621 in one-to-one correspondence, which not onlyimplement the connection between the planetary gear outer teeth casing613 and the planetary gear casing 62, but also ensure thecircumferential positioning of the planetary gear outer teeth casing 613and the planetary gear casing 62, and realize the synchronous operationof the planetary gear outer teeth casing 613 and the planetary gearcasing 62.

It will be appreciated that the positions of the plurality of flanges6131 and the positions of the plurality of latching slots 621 areinterchangeable, e.g., the plurality of flanges 6131 are all provided atthe inner circumferential wall of the planetary gear casing 62, and theplurality of latching slots 621 are all provided at the outer peripheralwall of the planetary gear outer teeth casing 613, or some of theplurality of flanges 6131 are provided on the outer peripheral wall ofthe planetary gear outer teeth casing 613, and some other of theplurality of flanges 6131 are provided on the inner peripheral wall ofthe planetary gear casing 62, and the plurality of latching slots 621are also provided correspondingly at the outer peripheral wall of theplanetary gear outer teeth casing 613 and the inner peripheral wall ofthe planetary gear casing 62 respectively, for convenient connection.

As shown in FIG. 7 , in conjunction with FIGS. 1, 21 and 23 , accordingto a still further embodiment of the present disclosure, the planetarygear assembly 6 further includes: a planetary gear bearing 63 providedin the planetary gear casing 62 and located on the outer side of theplanetary gear component 61, an inner ring of the planetary gear bearing63 is fitted over the main shaft 31 and rotates with the main shaft 31,an outer ring of the planetary gear bearing 63 is connected to theplanetary gear casing 62 and rotates with the planetary gear casing 62,and by providing the planetary gear bearing 63, it is ensured that theplanetary gear casing 62 rotates relative to the main shaft 31.

In one embodiment, an inner peripheral surface of the planet carrier 611is provided with meshing teeth that mesh with a second shaft 32 in themain shaft 31. Therefore, the planet carrier 611 is fixedly mounted tothe second shaft 32 to synchronously rotate with the second shaft 32.

In some examples, the second shaft 32 is supported by a second shaftbearing 3211 fitted over thereon and provided in the cavity 311. In oneembodiment, at least two second shaft bearings 3211 are provided in thecavity 311 of the main shaft 31, and the second shaft 32 passes throughthe at least two second shaft bearings 3211 to be supported in thecavity 311 of the main shaft 31 and to be rotatable with respect to themain shaft 31.

In some examples, the planetary gear assembly 6 further includes asecond shaft end bearing 3212. The planetary gear casing 62 is providedwith a through hole 622, the second shaft 32 passes through the throughhole 622, and the second shaft 32 is supported by a second shaft endbearing 3212 fitted thereon and provided in the through hole 622. Thus,one end of the planetary gear casing 62 is supported on the second shaft32 by the second shaft end bearing 3212, and the other end of theplanetary gear casing 62 is supported on the main shaft 31 by theplanetary gear bearing 63, which not only positions and mounts theplanetary gear assembly 6, but also ensure the rotation of the planetarygear casing 62 relative to the second shaft 32 and the main shaft 31.

In some examples, the planetary gear assembly 6 further includes a shaftsealing member 325, the shaft sealing member 325 is located in thethrough hole 622 and at an outer side of the second shaft end bearing3212. The shaft sealing member 325 is configured to seal a gap betweenthe second shaft 32 and the planetary gear casing 62.

In one embodiment, the shaft sealing member 325 is fitted over thesecond shaft 32, and is provided on the second shaft 32 and located atan outer side of the second shaft end bearing 3212. That is, the shaftsealing member 325 is further away from the axial center of the secondshaft 32 compared with the second shaft end bearing 3212, and the shaftsealing member 325 seals the gap between the second shaft 32 and theplanetary gear casing 62, which prevents water in the water supplypassage 320 of the second shaft 32 from entering the cavity 311 of themain shaft 31 and the planetary gear assembly 6 through the gap betweenthe second shaft 32 and the planetary gear casing 62.

The drum washing machine 100 according to embodiments of the presentdisclosure includes the planetary gear assembly 6 for a drum washingmachine.

Since the planetary gear assembly 6 for a drum washing machine accordingto embodiments of the present disclosure brings about the abovebenefits, i.e. by providing the planetary gear assembly 6 between themain shaft 31 and the agitator 4, the torque of the main shaft 31 can betransmitted to the agitator 4 to drive the agitator 4 to rotate, therotation of the agitator 4 may be combined with the rotation of the drum2 into various washing modes, to diversify the washing mode of the drumwashing machine 100.

Moreover, the torque of the main shaft 31 is transmitted to the agitatorby the planetary gear assembly 6, and the agitator 4 is driven by thedriver indirectly. Since the load of the agitator 4 is much less thanthe load of the drum 2, compared with the drum washing machine with animpeller in the related art, the load acting on the planetary gearassembly 6 is greatly reduced, which not only facilitates stable powertransmission to improve the performance stability of the drum washingmachine 100, but also greatly reduces the risk of damage to theplanetary gear assembly 6 to prolong the service life of the drumwashing machine 100.

Some embodiments of the drum washing machine 100 according to thepresent disclosure will be described in detail below with reference toFIGS. 1 to 23 .

As shown in FIGS. 1 to 23 , the drum washing machine 100 according toembodiments of the present disclosure includes a tub 1, a drum 2, anagitator 4, a driver (such as an electric motor 5 described below), anda planetary gear assembly 6.

The drum 2 is rotatably provided in the tub 1. The agitator 4 isrotatably provided in the drum 2. The driver is in transmissionconnection with the drum 2 via a main shaft 31 which transmits a torqueof the driver to the drum 2. The planetary gear assembly 6 is intransmission connection with the main shaft 31 and the agitator 4separately. When the driver drives the main shaft 31 to rotate, theplanetary gear assembly 6 may transmit the torque of the main shaft 31to the agitator 4, to drive the agitator 4 to rotate.

In the drum washing machine 100 according to the embodiment of thepresent disclosure, by providing the driver and driving the main shaft31 to rotate to drive the drum 2 to rotate using the driver, and furtherproviding the agitator 4 in the drum 2, and transmitting the torque ofthe main shaft 31 to the agitator 4 using the planetary gear assembly 6to drive the agitator 4 to rotate, the rotation of the agitator 4 may becombined with the rotation of the drum 2 into various washing modes, forexample, only one of the agitator 4 and the drum 2 is rotated or theagitator 4 and the drum 2 are rotated at the same time, or in the samedirection or in opposite directions to diversify the washing mode of thedrum washing machine 100.

Moreover, the driver drives the drum 2 via the main shaft 31, todirectly drive a component with a relatively large load using thedriver, the number of levels of power transmission is less, and thepower transmission is more direct, to stably drive the drum which islarge in volume and required to accommodate laundry and water. Theplanetary gear assembly 6 is provided between the main shaft 31 and theagitator 4, and the torque of the main shaft 31 is transmitted to theagitator by the planetary gear assembly 6 to indirectly drive theagitator 4 using the driver. Since the load of the agitator 4 is muchless than the load of the drum 2, compared with the drum washing machinewith an impeller (agitator) in the related art, the load acting on theplanetary gear assembly 6 is greatly reduced, which not only facilitatesstable power transmission to improve the performance stability of thedrum washing machine 100, but also greatly reduces the risk of damage tothe planetary gear assembly 6 to prolong the service life of the drumwashing machine 100.

Therefore, the drum washing machine 100 according to the embodiment ofthe present disclosure may implement various washing modes, and has theadvantages of stable performance, long service life, or the like.

The planetary gear assembly 6 of the drum washing machine 100 accordingto an embodiment of the present disclosure is switchable between a firststate and a second state.

The planetary gear assembly 6 in the first state transmits the torque ofthe main shaft 31 to the agitator 4 in the same direction, to rotate theagitator 4 and the drum 2 in the same direction. The planetary gearassembly 6 in the second state transmits the torque of the main shaft 31to the agitator 4 in an opposite direction, to rotate the agitator 4 andthe drum 2 in opposite directions. For example, if the driver drives themain shaft 31 to rotate clockwise, the planetary gear assembly 6 in thefirst state transmits the torque of the main shaft 31 to the agitator 4in the same direction, to rotate the agitator 4 and the drum 2clockwise. The planetary gear assembly 6 in the second state transmitsthe torque of the main shaft 31 to the agitator 4 in an oppositedirection, to rotate the agitator 4 counterclockwise.

For example, when the drum washing machine 100 is in a spin mode, theplanetary gear assembly 6 is switchable to the first state, and theagitator 4 and the drum 2 are driven to rotate in the same direction bythe mode of power transmission of the planetary gear assembly 6 in thefirst state, ensuring that the laundry will not be entangled or tornwhen spinning at a high speed.

When the drum washing machine 100 is in a wash mode, the planetary gearassembly 6 is switchable to the second state, and the agitator 4 and thedrum 2 are driven to rotate in opposite directions by the mode of powertransmission of the planetary gear assembly 6 in the second state, toagitate the laundry and water thoroughly to improve the effect ofcleaning the laundry.

In one embodiment, the combination of the state switching of theplanetary gear assembly 6 and the current mode of the drum washingmachine 100 is not limited to the above-mentioned embodiments, and thefirst and second states of the planetary gear assembly 6 may also becombined with any one of the spin and wash modes.

Thus, by providing the planetary gear assembly 6 which is switchablebetween the first and second states, the rotation direction of theagitator 4 is adjustable, and the agitator 4 and the drum 2 are rotatedin the same direction and in opposite directions, to cooperate with thedrum 2 to form operating modes suitable for different operatingconditions.

In some examples, when the agitator 4 and the drum 2 are rotated inopposite directions, the rotational speed of the agitator 4 is less thanthe rotational speed of the drum 2. That is, when the planetary gearassembly 6 is in the second state, the variable-speed transmission ofpower is implemented. Thus, when the laundry and the water aresufficiently agitated, the laundry is prevented from being entangled,and the stability and noise reduction of the whole machine arecontributed.

In some examples, when the agitator 4 and the drum are rotated in thesame direction, the rotational speed of the agitator 4 is equal to therotational speed of the drum 2. That is, when the planetary gearassembly 6 is in the first state, the agitator 4 is rotated insynchronization with the drum 2 (at the same speed and in the samedirection).

As shown in FIGS. 6-11 , according to an embodiment of the presentdisclosure, the planetary gear component 6 includes a planetary gearcomponent 61 and the planetary gear component 61 includes a planetcarrier 611, a plurality of planetary gears 612, and a planetary gearouter teeth casing 613.

The plurality of planetary gears 612 are rotatably mounted to the planetcarrier 611 respectively, and an outer peripheral wall of the main shaft31 has meshing teeth, and the plurality of planetary gears 612 aremeshed with the meshing teeth on the main shaft 31 respectively. Theplanetary gear outer teeth casing 613 is fitted over the plurality ofplanetary gears 612, and the planetary gear outer teeth casing 613 smeshes with the plurality of planetary gears 612 respectively, and theplanetary gear outer teeth casing 613 s is in transmission connectionwith the agitator 4.

It is understood that the inner peripheral wall of the outer casing 613of the planetary gear has meshing teeth that mesh with the plurality ofplanetary gears 612. Thus, the main shaft 31, the plurality of planetarygears 612, the planet carrier 611, the planetary gear outer teeth casing613 constitute a planetary gear train, and the shaft section of the mainshaft 31 meshing with the plurality of planetary gears 612 forms a sungear of the planetary gear train.

When the planet carrier 611 is allowed to rotate freely, the planetarygear assembly 6 is in the first state, and the agitator 4 and the drum 2are rotated in the same direction; when the planet carrier 611 isbraked, the planetary gear assembly 6 is in the second state, theplurality of planetary gears 612 are rotated respectively, and the outercasing 613 of the planetary gear and the main shaft 31 are rotated inopposite directions, to rotate the agitator 4 and the drum 2 in oppositedirections. Thus, by switching the state of the planet carrier 611 ofthe planetary gear assembly 6, the operating mode of the agitator 4 iscontrollable and the drum washing machine 100 is switchable amongvarious operating modes.

Thus, according to the drum washing machine 100 of the embodiment of thepresent disclosure, by providing planetary gear assembly 6 between themain shaft 31 and the agitator 4, and transmitting the torque of themain shaft 31 to the agitator 4 using the planetary gear assembly 6 todrive the agitator 4 to rotate, the rotation of the agitator 4 may becombined with the rotation of the drum 2 into various washing modes, forexample, only one of the agitator 4 and the drum 2 is rotated or theagitator 4 and the drum 2 are rotated at the same time, or in the samedirection or in opposite directions, to diversify the washing mode ofthe drum washing machine 100.

Moreover, the torque of the main shaft 31 is transmitted to the agitator4 by the planetary gear assembly 6, and the agitator 4 is driven by thedriver indirectly. Since the load of the agitator 4 is much less thanthe load of the drum 2, compared with the drum washing machine with animpeller (agitator) in the related art, the load acting on the planetarygear assembly 6 is greatly reduced, which not only facilitates stablepower transmission to improve the performance stability of the drumwashing machine 100, but also greatly reduces the risk of damage to theplanetary gear assembly 6 to prolong the service life of the drumwashing machine 100.

According to an embodiment of the present disclosure, the drum washingmachine 100 further includes a second shaft 32 and a brake 7, and thesecond shaft 32 meshes with the planet carrier 611, and the brake 7controls whether the planet carrier 611 is braked through the secondshaft 32.

In some examples, the side peripheral wall of the second shaft 32 isprovided with a spline. That is, the second shaft 32 forms a splineshaft, and the planet carrier 611 is provided with a spline grooveengaged with the spline of the second shaft 32, and the second shaft 32is fixedly connected with the planet carrier 611 through the engagementof the spline and the spline groove to ensure the synchronous operationof the second shaft 32 and the planet carrier 611.

When the brake 7 brakes the second shaft 32, the planet carrier 611 isbraked and unable be rotated; when the brake 7 is disengaged from thesecond shaft 32, the planet carrier 611 is in a free state. Therefore,by providing the brake 7, the operating state of the second shaft 32 isswitchable, to switch the planetary gear assembly 6 between the firstand second states. The planetary gear assembly 6 switched between thefirst and second states may adjust the rotation direction of theagitator 4 to rotate the agitator 4 and the drum 2 in the same directionand in opposite directions, to cooperate with the drum 2 to formoperating modes suitable for different operating conditions.

In some examples, the main shaft 31 has a cavity 311 extending therethrough in the axial direction thereof, and the second shaft 32 passesthrough the cavity 311. For example, a central axis of the main shaft 31is parallel to and coincident with a central axis of the second shaft32, and the main shaft 31 is rotatable relative to the second shaft 32,to drive the drum 2 and the agitator 4 to rotate respectively to ensurethe normal operation of the drum washing machine 100.

As shown in FIGS. 12 to 21 , in some examples, a brake disk 322 is intransmission connection with the second shaft 32. When the brake 7 isfitted with the brake disk 322, the second shaft 32 is braked, torealize the braking of the planet carrier 611. When the brake 7 isdisengaged from the second shaft 32, the second shaft and the planetcarrier 611 are in a free state.

Furthermore, as shown in FIGS. 13 to 16 , the brake 7 includes: asliding groove seat 71, a brake lever 72, and a brake driver 73. Thesliding groove seat 71 is provided with a slideway 711. The brake lever72 is slidingly fitted with the slideway 711 between an extendingposition and a retracting position. The brake lever 72 is engaged withthe brake disk 322 in the extending position and disengaged from thebrake disk 322 in the retracting position. The brake driver 73 ismounted to the sliding groove seat 71 and is in transmission connectionwith the brake lever 72, and the brake driver 73 drives the brake lever72 to move between the extending position and the retracting position.Thus, by the brake driver 73 driving the brake lever 72 to move alongthe slideway 711, the brake lever 72 is engaged with and disengaged fromthe brake disk 322 and the switching is convenient.

In the brake 7 for a drum washing machine according to the embodiment ofthe present disclosure, the brake driver 73 drives the brake lever 72 tomove between the extending position and the retracting position. Byutilizing the brake lever 72 to be engaged with and disengaged from thebrake disk 322 on the second shaft 32 of the drum washing machine 100,the second shaft 32 is switched between the free state and the brakingstate, and then the torque of the main shaft 31 is transmitted to theagitator 4 through the planetary gear assembly 6 to drive the agitator 4to rotate. Thus, the rotation of the agitator 4 may be combined with therotation of the drum 2 into various washing modes to diversify thewashing mode of the drum washing machine 100.

Moreover, the brake 7 has a small number of parts and a simplerstructure. The brake driver 73 drives the brake lever 72 to move, thesecond shaft 32 is switched to the braking state by utilizing the brakelever 72 to be engaged with the brake disk 322 in the extendingposition, and the second shaft 32 is switched to the free state byutilizing the brake lever 72 to be disengaged from the brake disk 322 inthe retracting position. Therefore, compared with the drum washingmachine with an impeller in the related art, the brake lever 72 directlyacts on the brake disk 322 on the second shaft 32, which facilitatescontrol. Due to a small number of transmission structures between thebrake lever 72 and the second shaft 32, power transmission is moredirect, an operating state of the second shaft 32 may be stablyswitched, which facilitates stable transmission of power to improve theperformance stability of the drum washing machine 100.

Therefore, the brake 7 for a drum washing machine according to theembodiment of the present disclosure to switch a mode of the agitator 4collaborative with the drum 2 and has the advantages of a simplestructure, convenient control, stabilization, or the like.

In some examples, the brake lever 72 is provided with a limiting block720, and a limiting boss 712 is arranged in the slideway 711. Byarranging the limiting boss 712 in the slideway 711, the limiting boss712 is fitted with the limiting block 720 on the brake lever 72, amoving path of the brake lever 72 is limited. That is, the brake lever72 may be axially limited, which prevents the brake lever 72 fromsliding out of the slideway 711 to be detached from the sliding grooveseat 71, thus further ensuring the operating reliability of the brakelever 72.

In some examples, a circumferentially positioned sliding groove 713 isprovided in the slideway 711, and the limiting block 720 is slidablyfitted with the circumferentially positioned sliding groove 713. Byarranging the circumferentially positioned sliding groove 713 in theslideway 711, the limiting block 720 moves in the circumferentiallypositioned sliding groove 713 when the brake lever 72 moves along theslideway 711, and the circumferentially positioned sliding groove 713may circumferentially position the brake lever 72, realizinganti-rotation effect.

As shown in FIGS. 15 and 16 , in some examples, the brake lever 72includes: a slideway fitting portion 721, a transmission portion 722, abridge portion, and a brake portion 724.

The slideway fitting portion 721 is slidably fitted with the slideway711, and the transmission portion 722 is connected to a first end of theslideway fitting portion 721 while the bridge portion 723 is connectedto a second end of the slideway fitting portion 721. That is, both endsof the slideway fitting portion 721 are connected to the transmissionportion 722 and the bridge portion 723 respectively. The brake portionis connected to an end of the bridge portion away from the slidewayfitting portion 721, and the transmission portion 722 is in transmissionconnection with the brake driver 73, to drive the brake lever 72 to moveby driver. The brake portion 724 is engaged with the brake disk 322 whenthe brake lever 72 is in the extending position, while the brake portion724 is disengaged from the brake disk 322 when the brake lever 72 is inthe retracting position. The brake lever 72 has a simple structure andits connection with the sliding groove seat 71 and the brake driver isconvenient.

In some examples, a cross-section of the slideway fitting portion 721and a minimum cross-section of the slideway 711 are mutually matchedcircles. A cross-section of the bridge portion 723 is rectangular andits area is smaller than that of the slideway fitting portion 721.

That is to say, the cross-sectional area of the bridge portion 723 issmaller than the minimum cross-sectional area of the slideway 711, whichmay reduce a fitting area between an inner wall surface of the slideway711 and the brake lever 72, to reduce frictional force between the brakelever 72 and the sliding inner wall surface, and further reducing movingresistance to the brake lever 72.

In some examples, the bridge portion 723 is provided with a plurality oftransverse reinforcing ribs 7231 and a plurality of longitudinalreinforcing ribs 7232. Each transverse reinforcing rib 7231 extendsalong a width direction of the bridge portion 723 and the plurality oftransverse reinforcing ribs 7231 are spaced apart from each other alonga length direction of the bridge portion 723. Each longitudinalreinforcing rib 7232 extends along a length direction of the bridgeportion 723 and the plurality of longitudinal reinforcing ribs 7232 arespaced apart from each other along a width direction of the bridgeportion 723. Each longitudinal reinforcing rib 7232 is connected to theplurality of transverse reinforcing ribs 7231 respectively. By arrangingthe plurality of transverse reinforcing ribs 7231 and the plurality oflongitudinal reinforcing ribs 7232 on the bridge portion 723, thestructural strength of the bridge portion 723 is improved, and theservice reliability of the brake 7 is ensured, thus prolonging servicelife of the brake 7.

In some examples, the slideway fitting portion 721 is provided with aplurality of axial reinforcing ribs 7211. Each of the axial reinforcingribs extends along an axial direction of the slideway fitting portion721 and the plurality of the axial reinforcing ribs 7211 are spacedapart from each other along a circumferential direction of the slidewayfitting portion 721, to improve the structural strength of the slidewayfitting portion and further ensuring the service reliability of thebrake 7.

As shown in FIG. 13 , in some examples, a support sliding groove 714 isarranged in the slideway 711, and the transmission portion 722 isslidably supported on the support sliding portion 714.

In some examples, at least two support ribs protruding from an innersurface of the slideway 711 are arranged in the slideway 711, and eachof the support ribs extends along the length direction of the slideway711. A support sliding groove 714 is defined between adjacent supportribs, and the transmission portion 722 is supported on the support ribsand movable along the support sliding groove 714. Therefore, byarranging the supporting sliding portion 714 in the slideway 711, notonly the transmission portion 722 may be supported and positioned torealize the anti-rotation effect, but also a slidingly fittingreliability between the brake lever 72 and the sliding groove seat 71may be improved, which ensures normal operation of the driver.

According to another embodiment of the present disclosure, the brake 7further includes: a brake cam 74. The driver is configured as anelectric motor and is in transmission connected with the brake lever 72via the brake cam 74, and the brake cam 74 may convert a rotationalmotion of the electric motor shaft of the electric motor into a linearmotion of the brake lever 72 in the slideway 711 to ensure the normaloperation of the brake 7.

In some examples, the brake cam 74 is provided with an eccentric column741, the brake lever 72 is provided with a straight sliding groove 725,and the eccentric column 741 is in a sliding fit in the straight slidinggroove 725. When the electric motor drives the brake cam 74 to rotate,the eccentric column 741 of the brake cam 74 is eccentrically rotated,and since the slideway 711 limits the brake lever 72 to only movelinearly in its length direction, when the eccentric column 741 slidesin the straight sliding groove 725, the brake lever 72 is driven to movein the length direction of the slideway 711, with continuous operatingactions, and high use reliability.

In one embodiment, a length direction of the transmission portion 722 isperpendicular to a length direction of the bridge portion 723 and theslideway fitting portion 721. The straight sliding groove 725 isarranged on the transmission portion 722 of the brake lever 72 andextends along a length direction of the transmission portion 722, and alength direction of the straight sliding groove 725 is perpendicular toa linear motion direction of the brake lever 72 and the structure issimple and compact, which is convenient for fitting with the brake cam74, to realize the above functions.

In some examples, the sliding groove seat 71 is provided with a via hole715 in communication with the slideway 711, a part of the brake cam 74is arranged in the via hole 715 to be connected to the brake driver 73,and another part of the brake cam 74 extends into the slideway 711through the via hole 715, to facilitate the eccentric column 741 of thebrake cam 74 to cooperate with the straight sliding groove 725 of thebrake lever 72.

As shown in FIG. 12 , in some examples, the sliding groove seat 71 ismounted on a rear wall of the tub 1 through the brake support 75. Thebrake disk 322 is located on an outside of the tub 1 and is mounted onan end of the second shaft 32 extending out of the tub 1, and the brake7 is located on an outside of the tub 1, to cooperate with the brakedisk 322 to switch to different working modes of the drum washingmachine 100.

A side circumferential wall of the brake disk 322 has locking teetharranged along its circumferential direction, and the brake lever 72 ofthe brake 7 may be slidable between the extending position and theretracting position. The brake lever 72 abuts between two adjacentlocking teeth of the brake disk 322 in the extending position, and thebrake lever 72 is disengaged from the brake disk 322 is in theretracting position.

In some examples, the brake support 75 is provided with a limitingsliding groove 751 extending along an axial direction of the brake disk322. A portion of the brake lever 72 extending out of the slideway 711is slidably fitted in the limiting sliding groove 751, and the limitingsliding groove 751 limits the brake lever 72, which is used only usedfor guiding, but also ensures linear movement of the brake lever 72 toprevent the brake lever 72 from being broken during movement.

According to another embodiment of the disclosure, the drum washingmachine 100 further includes: a detector (not shown) for detecting powerof the driver. When the detector detects that the power of the driverreaches a predetermined value, the brake 7 controls whether the planetcarrier 611 is allowed to rotate freely through the second shaft 32, andthe agitator 4 and the drum 2 are rotated in the same direction, and thelaundry in the drum 2 is prevented from being entangled severely andtorn, with high safety.

As shown in FIGS. 1-3 , according to an embodiment of the presentdisclosure, the drum washing machine 100 further includes a drum support201 mounted to a rear wall of the drum 2 and located between the rearwall of the drum 2 and the rear wall of the tub 1, and the main shaft 31is rotatably connected with the drum 2 via the drum support 201 androtatably supported at the rear wall of the tub 1. That is, the mainshaft 31 may directly drive the drum 2 to rotate, and at the same time,the agitator 4 may be rotated by the planetary gear assembly 6, and theplanetary gear assembly 6 is not easily damaged.

In one embodiment, the drum 2 includes a drum body 21 with two openaxial ends and a rear cover 22 of the drum provided at a rear end of thedrum body 21. An outer periphery of the rear cover 22 of the drum isformed as a folded edge extending in an axial direction of the drum body21. The rear end of the drum body 21 is connected with the folded edgeof the rear cover 22 of the drum. A drum support 201 is fixed at thejoint of the drum body 21 and the folded edge of the rear cover 22 ofthe drum by a connecting member (for example, a screw), to fix the drum2 onto the drum support 201, and the drum 2 is rotatable with the drumsupport 201 relative to the tub 1.

In some examples, the drum support 201 has a central shaft portion 2011and a support portion 2012, and the central shaft portion 2011 extendsin the axial direction of the tub 1 and is rotatably supported on therear wall of the tub 1, the support portion 2012 is connected to theside peripheral wall of the central shaft portion 2011, and the drum 2is mounted to the support portion 2012.

In one embodiment, the support portion 2012 of the drum support 201includes a plurality of (for example, three) connecting arms distributedin the circumferential direction of the drum 2, each of the connectingarms extends in the radial direction of the drum 2, and an inner end ofeach of the connecting arms is connected with the side peripheral wallof the central shaft portion 2011, and an outer end of each of theconnecting arms is connected with the drum 2 through a connectingmember. The drum 2 is connected by using the plurality of connectingarms, which not only guarantees the reliability and stability ofconnection between the drum support 201 and the drum 2, but also reducesa material utilization amount of the drum support 201 and lowersmaterial costs and weight, to improve the cost performance of the drumwashing machine 100. It is understood that the support portion 2012 andthe central shaft portion 2011 may be integrally formed.

In some examples, the rear wall of the tub 1 is provided with a mountinghole 11, the mounting hole 11 is provided therein with a main shaftbearing seat 12, and the main shaft 31 is rotatably supported by themain shaft bearing 314 provided in the main shaft bearing seat 12. Thatis, the main shaft bearing seat 12 and the main shaft bearing 314mounted in the main shaft bearing seat 12 are provided in the mountinghole 11, the main shaft 31 extends into the mounting hole 11 in theaxial direction of the mounting hole 11 and is mounted to the rear wallof the tub 1 by the main shaft bearing 314, and thus, the main shaft 31is rotatable relative to the tub 1.

Referring to FIGS. 4 and 5 , and in conjunction with FIGS. 1, 21 and 23, in some examples, a main shaft sleeve 316 is fitted over the mainshaft 31, a main shaft flange 315 is fitted over the main shaft sleeve316, and the drum support 201 is connected to the main shaft flange 315,with convenient and reliable connection.

In one embodiment, the main shaft sleeve 316 is fitted over the mainshaft 31, the main shaft flange 315 is fitted over the main shaft sleeve316, and the drum support 201 is cast on the main shaft flange 315. Forexample, the drum support 201 may be a cast aluminum part. The mainshaft 31, the main shaft sleeve 316 and the main shaft flange 315 may beintegrally formed by machine work, which is advantageous for improvingthe production efficiency of the drum washing machine 100.

In some examples, an assembly sealing member 641 is fitted over theplanetary gear assembly 6 to seal a gap between the planetary gearassembly 6 and the main shaft flange 315, to guarantee the sealedconnection between the planetary gear assembly 6 and the main shaftflange 315.

Furthermore, the outer peripheral wall of the planetary gear assembly 6is provided with an annular limiting ring, the wear sleeve 642 is fittedover the planetary gear assembly 6 and one end is abutted against theannular limiting ring, the wear sleeve 642 is located between theplanetary gear assembly 6 and the assembly sealing member 641, theassembly sealing member 641 is formed in a ring shape and fitted overthe wear sleeve 642, an inner surface of the assembly sealing member 641is hermetically connected with the wear sleeve 642, and an outer surfaceof the assembly sealing member 641 is hermetically connected with themain shaft flange 315 and the drum support 201 respectively. Byproviding the wear sleeve 642 between the assembly sealing member 641and the planetary gear assembly 6, the wear sleeve 642 is engaged withthe assembly sealing member 641 to guarantee dimensional accuracy andimprove wear resistance.

As shown in FIG. 12 , according to an embodiment of the presentdisclosure, the main shaft 31 is in transmission connection with apulley 312, the driver is configured as an electric motor 5, and theelectric motor 5 drives the pulley 312 to rotate by a belt 3121tensioned on the pulley 312, i.e., the belt 312 is wound on the electricmotor shaft 51 and the pulley 312. Thus, by providing the pulley 312 andthe belt 3121 on the main shaft 31, the transmission connection betweenthe main shaft 31 and the driver is realized by the belt 3121, whichcushions impact and attenuates vibration load, smooths the operation ofthe main shaft 31, and reduces the noise generated during operation.

In some examples, the pulley 312, the belt 3112 and the driver are alllocated outside the tub 1, and the pulley 312 is stopped between therear wall of the tub 1 and a lock nut 313 on the main shaft 31. That is,the pulley 312 is fixedly connected to the main shaft 31 and locatedbetween the rear wall of the tub 1 and the lock nut 313. By providingthe lock nut 313, the pulley 312 may be positioned and mounted, and thedriver drives the pulley 312 to rotate through the belt 3121, and thepulley 312 drives the main shaft 31 to rotate, to achieve synchronousrotation of the pulley 312 with the main shaft 31.

As shown in FIGS. 22 and 23 , according to another embodiment of thepresent disclosures, the agitator 4 has a water spray hole 41, the drumwashing machine 100 further includes a water supply device (not shown),the water supply device is in communication with the tub 1 and theagitator 4 separately, and the water supply device supplies the water inthe tub 1 to the agitator 4 and sprays water into the drum 2 through thewater spray hole 41.

In the process of washing the laundry, the water supply device supplieswater to the agitator 4, and water is sprayed to the laundry in the drum2 through the water spray hole 41, to wet the laundry and improving thelaundry wetting effect. The agitator 4 may agitate the water in the drum2, which diversifies the washing mode of the drum washing machine 100,to improve the laundry washing effect and facilitating the reduction ofthe washing time.

According to some embodiments, the water supply device includes a watersupply pipe and a water supply pump, and the water supply pipe has afirst end and a second end. The first end of the water supply pipe is incommunication with the tub 1, and the second end of the water supplypipe is connected to the agitator 4, to supply the water in the tub 1 tothe agitator 4 through the water supply pipe. Herein, the term“connected” in the expression “the second end of the water supply pipeis connected to the agitator 4” should be understood broadly. Forexample, the water supply pipe may or may not be physically connected tothe agitator 4, as long as the water from the second end of the watersupply pipe may be supplied to the agitator 4.

Thus, the water in an inner cavity of the tub 1 is supplied to theagitator 4 through the water supply pipe, and the laundry may be wetted,and the laundry wetting effect is improved. By communicating the watersupply device with the inner cavity of the tub 1, the laundry may bewetted by the washing water in the tub 1, without an additional watersource, reducing the water consumption. It is understood that in somemodels without a circulating pump, the first end of the water supplypipe may also be directly connected to the water supply source for watersupply, such as an external faucet, instead of using circulating waterin the washing machine.

In some examples, the first end of the water supply pipe is incommunication with a bottom of the inner cavity of the tub 1. In thisway, the water supply pump may pump the water at the bottom of the innercavity of the tub 1 to the agitator 4, and even if the drum washingmachine 100 is in the washing mode with the lowest water level, thewater supply device may still ensure the water supply to the agitator 4,to guarantee the wetting and washing effects of the drum washing machine100 in different washing modes.

In some examples, the agitator 4 has a water collection cavity 42 and awater dividing passage 43 inside, and the water collection cavity 42 isin communication with the water supply device, and the water spray hole41 is in communication with the water collection cavity 42 through thewater dividing passage 43. By providing the water collection cavity 42and the water dividing passage 43 in the agitator 4, the water supplydevice may transport the water to the water collection cavity 42 and thewater dividing passage 43, and finally water is sprayed through thewater spray hole 41 into the drum 2, to wet the laundry, and improvingthe laundry wetting effect and the washing effect.

In some examples, the surface of the agitator 4 facing the interior ofthe drum 2 is provided with a plurality of ribs 44, each of the ribs 44extends in the radial direction of the agitator 4 and the plurality ofribs 44 is spaced apart from each other in the circumferential directionof the agitator 4. The water spray hole 41 is defined on the rib 44.When the laundry is washed, the water is sprayed toward the inner cavityof the drum 2 through the water spray hole 41, and the rib 44 enablesthe water in the drum 2 to generate a vortex to drive the laundry torotate and turn over, to improve the laundry washing effect.

In some examples, the agitator 4 is configured as an impeller. That is,the impeller is provided at the bottom of the drum 2 of the drum washingmachine 100. In the process of washing the laundry, the laundry in thedrum 2 is lifted up and dropped continuously, and thus may be cleaned.Simultaneously, under the action of the impeller, the drum washingmachine 100 according to the present disclosure is provided additionallywith the impeller to rub the laundry based on the conventional method ofdropping-washing the laundry (only with rotation of the drum), tofurther improve the washing effect and shortening the washing time.

As shown in FIGS. 21 and 23 , in other examples, the second shaft 32 hasa water supply passage 320 therein, and the water supply device supplieswater in the tub 1 to the agitator 4 through the water supply passage320. By providing the water supply passage 320 in the second shaft 32,the second shaft 32 has a function of transporting water, to transportthe washing water in the tub 1 into the water supply passage 320 of thesecond shaft 32 through the water supply device, and finally sprayingwater through the water spray hole 41 into the tub 1.

In some examples, an end of the second shaft 32 extending out of the tub1 is provided with an adapter 323, and the water supply device isconnected with the second shaft 32 via the adapter 323. By providing theadapter 323 at the end of the second shaft 32 extending out of the tub1, a water supply end of the water supply passage 320 is sealed, and thewater supply device transports the water in the tub 1 into the watersupply passage 320.

In some examples, the adapter 323 is fitted over one end of the secondshaft 32 extending out of the tub 1, an adapter bearing 3231 is providedbetween the adapter 323 and the second shaft 32, an inner ring of theadapter bearing 3231 is fixedly connected with the second shaft 32, theouter ring of the adapter bearing 3231 is fixedly connected with theadapter 323, and the adapter bearing 3231 may be configured as two ballbearings arranged side by side, or a roller bearing. Thus, the rotatableconnection between the second shaft 32 and the adapter 323 is realizedby the adapter bearing 3231.

Advantageously, an adapter sealing member 3232 is fitted over the end ofthe second shaft 32 extending out of the tub 1, the adapter sealingmember 3232 is further away from an axial center of the second shaft 32compared with the adapter bearing 3231. The adapter sealing member 3232seals a gap between the second shaft 32 and the adapter 323.

In one embodiment, the adapter sealing member 3232 and the adapterbearing 3231 are fitted over the end of the second shaft 32 extendingout of the tub 1, and the adapter sealing member 3232 and the adapterbearing 3231 are arranged along an axial direction of the second shaft,and the adapter sealing member 3232 is located on an outside of theadapter bearing 3231. The adapter sealing member 3232 is sealedlyconnected to the second shaft 32 and the adapter 323 separately, toensure a sealed connection between the adapter 323 and an outer sidewall of the second shaft 32 and prevent water in the water supplypassage 320 of the second shaft 32 from entering the cavity 311 of themain shaft 31, which otherwise affects normal operations of othercomponents.

In some examples, a wear ring 324 is provided in the adapter 323, andthe wear ring 324 is embedded in an inner side of the adapter 323. Theend of the second shaft 32 extending out of the tub 1 extends into thewear ring 324, and both the adapter bearing 3231 and the adapter sealingmember 3232 are fitted over the second shaft 32 and are located betweenan outer side wall of the second shaft 32 and the wear ring 324.

That is, the wear ring 324 is located between the adapter 323 and theadapter bearing 3231 and between the adapter 323 and the adapter sealingmember 3232. By arranging the wear ring 324 in the adapter 323, an outerring of the adapter bearing 3231 and the adapter sealing member 3232 arefitted with the wear ring 324 to reduce wear of the adapter 323 andprolong service life of thee adapter 323.

In some examples, a shaft sealing member 325 is fitted over the secondshaft 32, and is provided on the second shaft 32 and located at an outerside of a second shaft end bearing 3212. That is, the shaft sealingmember 325 is further away from the axial center of the second shaft 32compared with the second shaft end bearing 3212, and the shaft sealingmember 325 seals the gap between the second shaft 32 and the planetarygear casing 62, which prevents water in the water supply passage 320 ofthe second shaft 32 from entering the cavity 311 of the main shaft 31and the planetary gear assembly 6 through the gap between the secondshaft 32 and the planetary gear casing 62.

Some embodiments of the drum washing machine 100 according to thepresent disclosure will be described in detail below with reference toFIGS. 1 to 23 .

As shown in FIGS. 1, 21 and 23 , the drum washing machine 100 accordingto an embodiment of the present disclosure includes: a tub 1, a drum 2,a main shaft 31, a second shaft 32, a driver (such as an electric motor5 described below), a planetary gear assembly 6 and a brake 7.

The tub 1 extends in a front and rear direction and has an open frontend. The rear wall of the tub 1 is provided with a mounting hole 11penetrating in a thickness direction thereof, and the mounting hole 11is provided therein with a main shaft bearing seat 11 extending in theaxial direction thereof.

The main shaft 31 extends in the front and rear direction and has acavity 311 extending in the axial direction thereof, and the main shaft31 passes through the main shaft bearing seat 11 through two spaced mainshaft bearings 314. One end (front end shown in FIG. 1 ) of the mainshaft 31 extending out of an inner surface of the rear wall of the tub 1is fixedly connected with the drum support 201, and one end (rear endshown in FIG. 1 ) of the main shaft 31 extending out of an outer surfaceof the rear wall of the tub 1 is connected with the lock nut 313, thepulley 312 for mounting the belt 3121 is provided between the lock nut313 and the outer surface of the rear wall of the main shaft 31, and thepulley 312 is in transmission connection with the electric motor shaft51 of the electric motor 5 through the belt 3121.

The drum 2 includes the drum body 21 and the rear cover 22 of the drum.The drum body 21 extends in the axial direction of the tub 1 and has twoopen ends. The rear cover 22 of the drum is hermetically connected atthe rear end of the drum body 21, and the drum 2 is rotatably mounted inthe tub 1 by the drum support 201. The drum support 201 includes acentral shaft portion 2011 and a support portion 2012 connected to anouter side wall of the central shaft portion 2011. The drum 2 issupported on the support portion 2012, and the central shaft portion2011 is rotatably supported on the rear wall of the tub 1.

The second shaft 32 passes through the cavity 311 of the main shaft 31by at least two second shaft bearings 3211 spaced apart in the axialdirection thereof. The two ends of the second shaft 32 extend out of thetwo ends of the main shaft 31 respectively, one end (front end shown inFIG. 1 ) of the second shaft 32 extending out of the main shaft 31 isfitted with the planetary gear assembly 6 through the second shaft endbearing 3212, and the shaft sealing member 325 located at an outer sideof the second shaft end bearing 3212 is further provided between theplanetary gear assembly 6 and the second shaft 31, to guarantee thesealed connection between the planetary gear assembly 6 and the secondshaft 31. The other end (such as a rear end shown in FIG. 1 ) of thesecond shaft 32 extending out of the main shaft 31 is mounted with thebrake disk 322.

The agitator 4 is rotatably provided at the bottom of the drum 2 andcooperates with the planetary gear assembly 6 (such as the planetarygear casing 62 described below).

The planetary gear assembly 6 of the drum washing machine 100 accordingto the embodiment of the present disclosure will be described in detailbelow.

The planetary gear assembly 6 includes the planetary gear component 61,the planetary gear casing 62, and the planetary gear bearing 63. Theplanetary gear casing 62 has a through hole 622, the planetary gearcomponent 61 is provided in the planetary gear casing 62, the planetarygear bearing 63 is provided in the planetary gear casing 62 and islocated on a side of the planetary gear casing 62 back on to the throughhole 622, and the planetary gear bearing 63 is provided at the rear ofthe planetary gear casing 62.

The planetary gear component 61 includes the planet carrier 611, threeplanetary gears 612, and the planetary gear outer teeth casing 613. Theplanet carrier 611 includes the planetary gear support 6111 and theplanetary gear fixing disk 6116. One side of the planetary gear support6111 is provided with the plurality of mounting bosses 6112 and theplurality of planetary gear mounting seats 6114. The plurality ofmounting bosses 6112 and the plurality of planetary gear mounting seats6114 are arranged alternately in the circumferential direction of theplanet carrier 611. Each of the planetary gear mounting seats 6114 isprovided with the planetary gear fixing shaft 6115. One end of theplanetary gear fixing shaft 6115 is provided in the planetary gearmounting seat 6114, and the other end is provided in the limiting hole6118 of the planetary gear fixing disk 6116, suitable to be engaged andconfigured to mount the planetary gear 612; each of the mounting bosses6112 is provided with the positioning column 6113, and the planetarygear fixing plate 6116 is provided with the positioning hole 6117engaged with the positioning column 6113. By welding the positioningcolumn 6113 at the positioning hole 6117, or make the positioning column6113 close fit with the positioning hole 6117, the planetary gear fixingplate 6116 is connected to the planetary gear support 6111. The threeplanetary gears 612 are mounted on the planet carrier 611 and mesh withthe planetary gear outer teeth casing 613 respectively.

The planetary gear outer teeth casing 613 of the planetary gearcomponent 61 is provided with the flange 6131 protruding from the outersurface, and the inner surface of the planetary gear casing 62 isprovided with the latching slot 621 engaged with the flange 6131, tofixedly connect the planetary gear outer teeth casing 613 with theplanetary gear casing 62.

The planetary gear assembly 6 is rotatably fitted to the second shaft 32via the second shaft end bearing 3212. The planetary gear assembly 6 isrotatably fitted to the main shaft 31 via the planetary gear bearing 63.In one embodiment, the main shaft sleeve 316 is fitted over the mainshaft 31, the main shaft sleeve 316 is provided with the main shaftflange 315 connected to the drum support 201, the wear sleeve 642 isfitted over the planetary gear assembly 6, the wear sleeve 624 isprovided with the assembly sealing member 641, and the sealedconnections between the planetary gear assembly 6 and the drum support201 as well as the planetary gear assembly 6 and the main shaft flange315 are realized by the assembly sealing member 641.

The brake 7 of the drum washing machine 100 according to an embodimentof the present disclosure will be described in detail below.

The brake 7 is arranged at a rear portion of the tub 1 and includes asliding groove seat 71, a brake lever 72, a brake driver 73 and a brakecam 74.

The sliding groove seat 71 is arranged on a rear wall of the tub 1through a brake support 75, and the brake support 75 is provided with alimiting sliding groove 751 extending along a radial direction of brakedisk 322. A linearly extending slideway 711, a circumferentiallypositioned sliding groove 713, and a support sliding groove 714 arearranged in the sliding groove seat 71 is provided with. A limiting boss712 is arranged in the slideway 711, and the sliding groove seat 71 isalso provided with a via hole 715 in communication with the slideway711.

The brake lever 72 is slidably fitted with the slideway 711 between theextending position and the retracting position. The brake lever 72includes a slideway fitting portion 721, a transmission portion 722, abridge portion 723, and a brake portion 724. The two ends of theslideway fitting portion 721 are connected with the transmission portion722 and the bridge portion 723 respectively, and the brake portion 724is connected to an end of the bridge portion 723 away from the slidewayfitting portion 721.

The slideway fitting portion 721 is slidably fitted with the slideway711, and a cross-section of the slideway fitting portion 721 and aminimum cross-section of the slideway 711 are mutually matched circles.The slideway fitting portion 721 is provided with a plurality of axialreinforcing ribs 7211. Each of the axial reinforcing ribs extends alongan axial direction of the slideway fitting portion 721 and a pluralityof the axial reinforcing ribs 7211 are spaced apart from each otheralong a circumferential direction of the slideway fitting portion 721.

The transmission portion 722 is slidably supported on the supportsliding groove 714. A side of the transmission portion 722 is providedwith a limiting block 720 slidably fitted with the circumferentiallypositioned sliding groove 713. By arranging the limiting boss 712 in theslideway 711 to be fitted with the limiting block 720 on the brake lever72, a moving path of the limiting lever 72 is limited. That is, thebrake lever 72 may be axially limited to prevent the brake lever 72 fromsliding out of the slideway 711, thus further ensuring the operatingreliability of the brake 7. Another side of the transmission portion 722is provided with a straight sliding groove 725.

The bridge portion 723 is provided with a plurality of transversereinforcing ribs 7231 and a plurality of longitudinal reinforcing ribs7232. Each transverse reinforcing rib 7231 extends along a widthdirection of the bridge portion 723 and the plurality of transversereinforcing ribs 7231 are spaced apart from each other along a lengthdirection of the bridge portion 723. Each longitudinal reinforcing rib7232 extends along a length direction of the bridge portion 723 and theplurality of longitudinal reinforcing ribs 7232 spaced apart from eachother along a width direction of the bridge portion 723. Eachlongitudinal reinforcing rib 7232 is connected to the plurality oftransverse reinforcing ribs 7231 respectively.

The brake portion 724 is engaged with the brake disk 322 when the brakelever 72 is in the extending position, while the brake portion 724 isdisengaged from the brake disk 322 when the brake lever 72 is in theretracting position.

The brake cam 74 is mounted at the via hole 715 of the sliding grooveseat 71 and has an eccentric column 741. The brake driver 73 is used todrive the brake cam 74 to rotate, and the eccentric column 741 rotateseccentrically. The eccentric column 741 is fitted with the straightsliding groove 725 on the transmission portion 722 to further drive thebrake lever 72 to move linearly.

According to another embodiment of the present disclosure, an end of thesecond shaft 32 extending out of the tub 1 is provided with an adapter323 for connecting the water supply device. The adapter 323 is fittedover the second shaft 32 through the adapter bearing 3231, and theadapter sealing member 3232 sealingly connected to the adapter 323 isfitted over the second shaft 32. The adapter sealing member 3232 islocated on an outside of the adapter bearing 3231.

Furthermore, the water supply passage 320 is provided in the secondshaft 32 and extends along the axial direction of the second shaft 32. Afirst end of the water supply passage 320 is in communication with theadapter 323, and a second end of the water supply passage 320 is incommunication with the agitator 4. The agitator 4 has the watercollection cavity 42 to be in communication with the water supplypassage 320, the water dividing passage 43 defined by the rib 44, andthe water spray hole 41 defined on the rib 44.

The water supply device includes the water supply pipe and the watersupply pump. The first end of the water supply pipe is in communicationwith the tub 1, the second end of the water supply pipe is incommunication with the water supply passage 320, and the water supplypump is arranged on the water supply pipe, and when the water supplypump is working, the water in the tub 1 is conveyed into the agitator 4via the water supply pipe and the water supply passage 320.

The working process of the drum washing machine 100 according to anembodiment of the present disclosure will be described in detail below.

When the drum washing machine 100 is operating in the washing mode, thebrake driver 73 drives the brake lever 72 to move to the extendingposition, and the brake portion 724 of the brake lever 72 is engagedwith the brake disk 322 to lock the brake disk 322, and the second shaft32 is fixed, and since the planet carrier 611 of the planetary gearassembly 6 is fitted with the second shaft 32 by a spline structure, theplanet carrier 611 is also fixed, and only the plurality of planetarygears 612 on the planet carrier 611 are rotatable on their own axes.

Subsequently, when the electric motor 5 is in operation, the pulley 312is driven to rotate in a forward direction by the belt 3121, and themain shaft 31 and the drum 2 are driven to rotate in the forwarddirection. Since the main shaft 31 meshes with the plurality ofplanetary gears 612, the main shaft 31 may simultaneously drive theplurality of planetary gears 612 to rotate when rotating, which furtherdrives the planetary gear outer teeth casing 613 to rotate in theopposite direction. Since the planetary gear outer teeth casing 613 isconnected with the planetary gear casing 62 and the planetary gearcasing 62 is connected with the agitator 4, the main shaft 31 drives theagitator to rotate in the opposite direction by the planetary gearassembly 6.

In this process, the laundry in the drum 2 is lifted up and droppedcontinuously, and thus may be washed clean. Simultaneously, under theaction of the agitator 4, the drum washing machine 100 according to thepresent disclosure is provided additionally with the impeller to rub thelaundry based on the conventional method of dropping and washing thelaundry (only the drum is rotated), to further improve the washingeffect and shortening the washing time.

When the agitator 4 has the water spray hole 41, the water supply pumpmay supply water to the agitator 4 through the water supply passage 320of the second shaft 2 or through the water supply pipe, to cause thewater spray hole 41 to spray water to the laundry in the drum 2, whichwets the laundry, improves the laundry wetting effect, and furtherimproves the laundry washing effect.

It is understood that when the drum washing machine 100 is in thewashing mode, the planetary gear assembly 6 transmits the forwardrotation of the main shaft 31 as the reversed rotation of the agitator4, and at the same time, the planetary gear assembly 6 is intransmission connection with the main shaft 31, which may reduce thespeed of the main shaft 31, to make the rotational speed of the agitator4 less than the rotational speed of the main shaft 31. Here, the“forward rotation” and “reversed rotation” are relative terms and do notrefer to a counterclockwise or clockwise rotation.

When the drum washing machine 100 is operating in the spin mode, thebrake driver 73 drives the brake lever 72 to move to the retractingposition, the brake portion 724 of the brake lever 72 releases the brakedisk 322, and the second shaft 32 is in the free state.

Subsequently, when the electric motor 5 drives the pulley 312 to rotatein the forward direction through the belt 3121, the main shaft 31 andthe drum 2 may be driven to rotate in the forward direction, and thenthe main shaft 31 drives the planetary gear 612 to rotate on its axis,to drive the planetary gear casing 62, the agitator 4 and the drum 2 torotate in the same direction and at the same speed.

In the drum washing machine 100 according to the embodiment of thepresent disclosure, by providing the driver, the driver drives the drum2 via the main shaft 31, the number of levels of power transmission isless, and the power transmission is more direct, to stabilize theoperation of the drum 2. The planetary gear assembly 6 is providedbetween the main shaft 31 and the agitator 4, and the torque of the mainshaft 31 is transmitted to the agitator 4 by the planetary gear assembly6. Since the load of the agitator 4 is much less than the load of thedrum 2, compared with the drum washing machine with an impeller in therelated art, the load acting on the planetary gear assembly 6 is greatlyreduced, which greatly reduces the risk of damage to the planetary gearassembly 6 to prolong the service life of the drum washing machine 100.

Other components and operations of the drum washing machine 100according to the embodiments of the present disclosure are known andwill not be described in detail herein.

In the description of the present specification, reference throughoutthis specification to “an embodiment”, “some embodiments”, “exemplaryembodiment”, “example”, “specific example” or “some examples” means thata particular feature, structure, material, or characteristic describedin connection with the embodiment or example is included in at least anembodiment or example of the present disclosure. In the specification,the schematic expressions to the above-mentioned terms are notnecessarily referring to the same embodiment or example. Furthermore,the described particular features, structures, materials, orcharacteristics may be combined in any suitable manner in one or moreembodiments or examples.

What is claimed is:
 1. A planetary gear assembly for a drum washingmachine, comprising: a planetary gear component and a planetary gearcasing, wherein the planetary gear component comprises: a planetcarrier; a plurality of planetary gears rotatably mounted to the planetcarrier separately and configured to be meshed with a main shaftseparately, the main shaft being configured to drive a drum to rotate ina drum washing machine; and a planetary gear outer teeth casing fittedover an outer side of the plurality of planetary gears, meshed with theplurality of planetary gears separately, and configured to be intransmission connection with an agitator in the drum; wherein theplanetary gear component is provided in the planetary gear casing, andthe planetary gear outer teeth casing is in transmission connection withthe agitator via the planetary gear casing.
 2. The planetary gearassembly according to claim 1, wherein when the planet carrier isallowed to rotate freely, the plurality of planetary gears transmit atorque of the main shaft to the planetary gear outer teeth casing in asame direction, and when the planet carrier is braked, the plurality ofplanetary gears transmit the torque of the main shaft to the planetarygear outer teeth casing in an opposite direction.
 3. The planetary gearassembly according to claim 2, wherein when the planet carrier isbraked, a rotational speed of the planetary gear outer teeth casing isless than a rotational speed of the main shaft.
 4. The planetary gearassembly according to claim 2, wherein when the planet carrier isallowed to rotate freely, a rotational speed of the planetary gear outerteeth casing is equal to a rotational speed of the main shaft.
 5. Theplanetary gear assembly according to claim 2, wherein the planet carriercomprises: a planetary gear support, wherein the plurality of planetarygears are rotatably mounted on a side face of the planetary gearsupport, and the side face of the planetary gear support is providedwith a plurality of mounting bosses; and a planetary gear fixing diskmounted on the plurality of mounting bosses.
 6. The planetary gearassembly according to claim 5, wherein the planetary gear support andthe planetary gear fixing disk are both located in the planetary gearouter teeth casing, and the planetary gear support and the planetarygear fixing disk are stopped at two sides of internal teeth of theplanetary gear outer teeth casing respectively to be positioned in anaxial direction of the planetary gear outer teeth casing.
 7. Theplanetary gear assembly according to claim 5, wherein the side face ofthe planetary gear support is provided with a plurality of planetarygear mounting seats, each of the planetary gear seats is provided with aplanetary gear fixing shaft, and the plurality of planetary gears arerotatably mounted to the plurality of planetary gear fixing shafts inone-to-one correspondence respectively.
 8. The planetary gear assemblyaccording to claim 5, wherein the plurality of mounting bosses and theplurality of planetary gears are arranged alternately in acircumferential direction of the planetary gear support, each of themounting bosses is provided with a positioning column, the planetarygear fixing disk is provided with a plurality of positioning holes, andpositioning columns on the plurality of mounting bosses are fitted inthe plurality of positioning holes in one-to-one correspondence.
 9. Theplanetary gear assembly according to claim 1, wherein one of an innerperipheral wall of the planetary gear casing and an outer peripheralwall of the planetary gear outer teeth casing is provided with a flange,another one of the inner peripheral wall of the planetary gear casingand the outer peripheral wall of the planetary gear outer teeth casingis provided with a latching slot, and the flange is fitted in thelatching slot.
 10. The planetary gear assembly according to claim 9,wherein the outer peripheral wall of the planetary gear outer teethcasing is provided with a plurality of flanges, each of the flangesextends in an axial direction of the planetary gear outer teeth casing,the plurality of flanges are spaced apart from each other in acircumferential direction of the planetary gear outer teeth casing, theinner peripheral wall of the planetary gear casing is provided with aplurality of latching slots, each of the latching slots extends in anaxial direction of the planetary gear casing, the plurality of latchingslots are spaced apart from each other in a circumferential direction ofthe planetary gear casing, and the plurality of flanges are fitted inthe plurality of latching slots in one-to-one correspondence.
 11. Theplanetary gear assembly according to claim 1, further comprising: aplanetary gear bearing provided in the planetary gear casing and locatedon an outer side of the planetary gear component, wherein an inner ringof the planetary gear bearing is fitted over the main shaft and rotateswith the main shaft, and an outer ring of the planetary gear bearing isconnected to the planetary gear casing and rotates with the planetarygear casing.
 12. The planetary gear assembly according to claim 1,wherein an inner peripheral surface of the planet carrier is providedwith meshing teeth meshing with a second shaft in the main shaft. 13.The planetary gear assembly according to claim 12, further comprising asecond shaft end bearing, wherein the planetary gear casing is providedwith a through hole, the second shaft passes through the through hole,and the second shaft end bearing is provided in the through hole andconfigured to support the second shaft.
 14. The planetary gear assemblyaccording to claim 13, further comprising a shaft sealing member locatedin the through hole and at an outer side of the second shaft endbearing, and configured to seal a gap between the second shaft and theplanetary gear casing.
 15. A drum washing machine comprising a planetarygear assembly, wherein the planetary gear assembly comprises: aplanetary gear component and a planetary gear casing, wherein theplanetary gear component comprises: a planet carrier; a plurality ofplanetary gears rotatably mounted to the planet carrier separately andconfigured to be meshed with a main shaft separately, the main shaftbeing configured to drive a drum to rotate in a drum washing machine;and a planetary gear outer teeth casing fitted over an outer side of theplurality of planetary gears, meshed with the plurality of planetarygears separately, and configured to be in transmission connection withan agitator in the drum; wherein the planetary gear component isprovided in the planetary gear casing, and the planetary gear outerteeth casing is in transmission connection with the agitator via theplanetary gear casing.